Door operator mechanism



Jan. 2s, 1964 M. CARLSON 3,119,310

DOOR OPERATOR MECHANISM Filed Nov. 15, 1960 3 Sheets-Sheet 1 GNN \9 INVENToR: MARTIN CARLSON BY Jan. 28, 1964 M, CARLSON DOOR OPERATOR MEOHANISM 3 Sheets-Sheet 2 Filed NOV. 15, 1960 INVENTOR.' MARTIN CARLSON ATTYS Jan. 28, 1964 M. CARLSON 3,119,310

DOOR OPERATOR MEOHANISM Filed Nov. 15, 1960 3 Sheets-Sheet 3 INVENTOR: MARTIN CARLSON United States PatentiOlice j 3,119,310 Patented dan. 28, 1964 3,1l910 DR ERATR MECHANISM Martin Carlson, 9122 13th St., Broolriield, lll. Filed Nov. 15, Mot), Ser. No. @,369 Claims. (Ci. 92-63) This invention relates to an improved door operator mechanism, and more particularly to an improved door operator mechanism which is power operated to both open and close the door and which is nonhanded in the sense that it may be externally adjusted to open the door in either direction after the mechanism has been installed. In particular, this invention relates to an improved mechanism for controlling the opening and closing movement of a door, which mechanism is related to those disclosed in my Patent No. 2,869,861, issued January 20, 1959, and in my copending patent application No. 863,213, filed December 31, 1959, now Patent No. 3,064,964.

The door operator of this invention has particular utility in conjunction with doors hung for pivotal movement about a generally vertical axis, the operator being completely concealed beneath the oor surface adjacent the door pivot axis.

Of necessity, door operator mechanisms designed to be completely concealed beneath the Hoor surface must re main small enough to be inconspicuous and inexpensive in installation and yet comprehend a wide variety of situations and circumstances of use which necessitate that such devices perform a multiplicity of functions.

Considering compact nature of door operators and the internal mechanism necessitated to achieve a multiplicity of functions, it is not surprising that most, if not all, previous operators have been single handed, that is, made specifically to accommodate only a right or a left handed door swing, but not adapted for both. Some of the more desirable operators permitted a slight variation in the design to accommodate either swing, although this choice had to be made at the time the operator was manufactured or else the unit had to be rebuilt after it was installed to achieve the opposite swing. None of these previous units permitted the hand of the door swing to be selected after the operator unit was installed for use.

Therefore, it is a particular object of this invention to provide a compact door operator including an internal mechanism suflicient to achieve a multiplicity of functions and yet be non-handed in the sense that the mechanism may be easily and eiiiciently adjusted externally, even after being installed, to provide either a right or a left handed door opening movement.

However, in order to achieve an effective non-handed door operator it is a paramount consideration that the mechanism be actuated positively in both directions and that the door movement be subject to externally adjustable control through a wide range, in order to achieve appropriate speeds through all phases of the door opening and closing operation, in both directions.

Thus, it is also a particular object of this invention to provide an eifective non-handed door operator of the type described which is externally adjustable to achieve the desired speed of door opening and closing movement during all phases of operation in both directions.

Further objects of the invention are to provide an improved dry-sump door operator mechanism adapted for full hydraulic power actuation of the door during both the opening and closing movements; to provide such a device which permits full utilization of casing space and provides maximum operator eiiiciency while providing for external adjustment to accomplish selectively either left handed or right handed door swing; to provide an irnproved hydraulic, double acting, door closer which is simple in operation, manufacture and repair and is inexpensive to maintain; and to provide such a device having a crossover safety valve system for permitting automatic reversal of door movement during any phase of opening and closing movement and for protecting the hydraulic system in cases where normal door movement may be physically blocked.

A specific embodiment of this invention is shown in the accompanying drawings in which:

Fil-SURE 1 is a plan view `of the subject door closer, with the cover removed, partly in section to show the piston operating in one yof the cylinders of the hydraulic actuating unit;

FIG. 2 is a partially sectioned elevational view of the same with the casing sectioned substantially on the plane of line 2-2 in FIGURE l;

FlG. 3 is an end elevational view of the twin cylinder support block of the hydraulic unit, as taken on the line 3 3 of FiG. l;

FlGS. 3A and 3B are to-p and end views respectively of the same;

FIGS. 4 and 4A are, respectively, an end elevational view and a side view of ia crossover relief valve unit `for the improved door closer, FIG. 4 being as seen from line 4-4 0f FIG. 1

FIG. 5 is a sectional elevational view showing the door spindle and crank assembly of the mechanism shown in FIGS. 1 and 2; and

FiG. 6 is a bottom face view of the door spindle drive flange.

ln the yform shown, the improved door closer mechanism is contained within a casing or housing 4, having upwardly extending side walls 6 and and end walls it) and 12 formed integrally therewith, the end walls being of generally arcuate con'guration. One end wall 1th` extends inwardly at its upper margin to form an arcuate radial flange portion 14 terminating in outer stop shoulders 16 and 18 having their faces spaced substantially apart. The flange portion 14 is further provided with an arcuate radially inwardly, projecting segment 2t), at the top center of the end wall 1d, forming opposing inner `stop shoulders 22 and 2Lihaving their faces spaced substmtially 309 apart for a purpose to be described.

Also, in the form shown, the mechanism of the door operator is comprised, generally, of ia spindle crank assembly 26 which is actuated to rotate in opposite directions by means of a twin hydraulic cylinder and piston unit 2.8 connected to diametrically opposite sides of the crank assembly 26 by connecting rods 27 and 27a. Hydraulic fluid pressure is utilized to selectively actuate the pistons of the twin cylinder unit for driving the crank assembly.

vMore particularly, a spindle 3i?, on which the door is mounted, extends downwardly into the casing d, adjacent one end thereof, where it is mounted for rotation in a step bearing comprising an upwardly rising boss 32 formed on the bottom of the inner casing d and Vhaving concentric bores the lowermost of which receives a reduced diameter lower end portion 34 of the spindle and the uppermost, or counter bore, receiving a thrust bearing 36 upon which the spindle shoulder 3S rests. The upper end of the spindle is supported and journaled within a top or cover plate di? (see FIG. 2) by -a radial bearing 42 retained within a bearing housing i4 threaded'ly received within an opening in the cover plate. An O-ring 45 m-ay also be provided to surround the spindle at the upper end of the bearing housing to provide a dirt seal.

l ust beneath the cover plate 4d, Ithe spindle 3d is drivingly connected to a spindle drive ilange 47 by means of splines or teeth i9 (see YFIG. 5). The spindle flange 47, is formed with an larcuate outwardly extending segment 53 `(see lFlG. 6) terminating in opposing stop shoul- Y ders 55 and y5'7 spaced approximately 240 apart, from face to face, and adapted to abut the spaced inner stop shoulders 22 and 24, respectively. '111e stop shoulders 2-24 and 55-57 limit the extent of the spindle rotation in each direction and thus limit the maximum swing of the door carried on the spindle 30, quite independently of the closure mechanism and the crank assembly 26, and thereby serve to protect the mechanism against inadvertent damage upon manual operation of the door, as in panic situations or when shifting from one hand to the other as will be later explained.

It is preferable, however, to provide for some adjustment of this maximum limit stop arrangement in order to accommodate special circumstances that might arise, such as a door handle hitting a wall adjacent the door opening or providing for clearance of the door, at maximum open position, from a projection on the adjacent wall. To accomplish this, adjustable abutment screws 59 and 61 may be provided in the stop shoulders 55 and 57 respectively. Each of the screws 59 and 61 is threaded into a bore normal to the face of the shoulder and is adjusted to allow only a predetermined angular movement of the spindle 30 for each direction of rotation. This adjustment is made with the cover removed, preferably precisely according to specification. Normally, and unless otherwise specified, the range of the door swing provided is 90 degrees on one side or the other of the centered or door closed position.

Rotatably mounted on the spindle 30 beneath the spindle flange 47 is a hub 63 (FIG. 5) constrained against axial movement with respect to the spindle by a thrust plate 65 resting `axially on a split collar 67 extending radially outwardly from an annular recess 69 formed in the spindle. The split collar 60 -is held in place by a retaining collar 71, which is also mounted on the spindle 30, the collar 71 being provided with a counter bore adjacent the upper end to receive the split collar 67.

`Mounted on the hub 63 and extending radially therefrom are three parallel, axially spaced crank plates 73, 75 and 77. The upper crank plate 73 is preferably integrally connected with hub 63, as by welding, for rotational movement therewith. As shown, the upper cuank plate 73 is substantially circular and is formed with an arcuate segment of its periphery cutaway to provide opposing radial stop shoulders 79 and 81, spaced apart substantially 150 degrees for contacting the aforementioned stop shoulders 22 `and 24 at opposite extreme positions of spindle rotation under power actuation by the pistoncylinder unit 28. This allows a normal rotation of 90 degrees for the spindle-crank assembly, between closed and open positions of the door, and yet serves as a permanent, built in, non-variable, limiting means to protect the hydraulic drive mechanism against damage from override.

An adjustable stop means for limiting the throw of the hydraulic actuator unit 28 is also desired, for the same reasons as in the case of the spindle flange 47, and in order to provide such a stop means an arcuate mounting block 83, projecting radially outward from the circumference of the upper crank plate 73 (FIGS. 1 and 5), is integrally formed thereon for engagement with the shoulders 16 and 18 of the casing ange 14. As shown, the mounting block 33 has at end faces and is provided with oppositely threaded bores 85 and 87 to receive, respectively, adjustment screws 89 and 91 which are provided with enlarged tiat heads 93 and 95. The heads of these screws may be of the Allen type, or have angularly spaced radial bores, to permit an appropriate tool to be inserted from above the mechanism to turn in the screw with respect to the mounting block. The respective adjustment screw heads 93 and 95 abut the stops 16 and 18 respectively at opposite ends of the desired limits for rotation of the spindle 30, thus determining the position of the door at the end of the opening and closing movements under the power of the actuating unit 28. Adjustment of the screws 89 and 91 is made on the jo through an appropriate opening in the cover plate 40 .4 which normally may be closed by a removable member 97.

The intermediate crank plate 75 and the lower crank plate 77 are generally circular in plan view, the intermediate crank plate 75 being formed integrally with, or welded or splined to rotate with, the hub 63. As shown in FIG. 5, the lower crank plate 77 is carried by the crank plates 73 and 75 and the assembly is held together by the crank pins 99 and 101 (shown only in FIG. l), a stress balancing spacer pin 103, and the housings for the breakaway pins to be now described.

As is best seen in FIGURE 5, the upper crank plate 73, intermediate crank plate 75, and lower crank plate 77 are each appropriately formed with aligned spaced apertures for receiving pin housings 105, 107 and 109 extending through and firmly secured to the respective crank plates.

Each pin housing is hollow and provided at its lower end with an inwardly tapered internal shoulder forming a seat for a helical spring 115 which bears against an axially movable breakaway pin 117 which is normally urged upwardly against the bottom surface of the spindle ilange 47.

As shown, the pin housings 105, 107 and 109 are spaced angularly about the axis of the spindle 28, between the diametrically opposed crank pins 99 and 101, and on the far side of the spindle relative to the actuator 28. The pin housings 105 and 109 are spaced radially equidistant from the spindle axis and substantially degrees apart. The pin housing 107 is located angularly midway between the pin housings and 109 and is on a different or shorter radius than the other two pin housings. Also, the pin housing 107 is preferably located midway between the crank pins and diametrically opposite the spacer pin 103.

To ccact with the breakaway pins 117 the underside of the spindle flange 51 is provided with five equi-angularly spaced circular recesses 119, 121, 123, 125, and 127. As shown, the recesses 119, 123 and 127 are respectively 90 degrees apart and at the same radial distance from the spindle axis as the pin housings 105 and 109. The recesses 121 and 12S are also 90 degrees apart and are spaced radially from the spindle axis the same as the center breakaway pin 107.

Each recess in the spindle plate may be `further provided with a bushing 129, as shown in FIG. 5, having a frustro-conical seat for a tapered upper end on the breakaway pins 117. Thus, when the pins 117 are engaged with the bushings 129, under the action of the springs 115, the spindle plate 51 is rmly and drivingly engaged with the crank plate assembly; and yet, upon application of a greater force tending to turn the spindle 30, the pins will be cammed downwardly from their seats in the plate 47 and the plate 47 will thus be released from the crank assembly.

The purpose of the particular breakaway pin arrangement in the instant invention is to provide not only a means for permitting manual operation of the door in case of re or other emergency, even though the internal mechanism connected with the crank plates were to be frozen or otherwise inoperative, but also, to effect a change of the hand of the operator so as to permit it to be used with either right or left handed door swings, and to permit the selection of the swing direction to be made, even after installation, by a mere manual adjustment of the door itself.

Thus, in the arrangement shown in FIG. l, where the mechanism conditioned for a right-hand door opening operation is shown in the opened door position, and with the three breakaway assemblies spaced apart as before explained, the door carried by the spindle can be forced counter-clockwise to overcome the retentive action of the pins and once the breakaway of the spindle flange and the crank plate assembly occurs the door can be easily moved 90 degrees in the same direction with relationship to its former position to achieve a completely different or left handed swing; and only a reversal of the uid pressure source connections at A and B is required to accomodate the changed condition.

For example, if the pins in the housings 105, 107 and 109 are engaged respectively in the recesses 119, 121 and 123, of the spindle ange 47, as shown in FIG. l, an application of force on the door sulhcient to overcome the holding force of the breakaway means and turn the `spindle 'counter-clockwise will cause the spindle ilange 47 to shift in the same direction until it has moved through 90 degrees at which point the pins of the crank assembly, which has remained stationary, will engage in the recesses 123, 125 and 127 respectively. Now, upon reversal of the pressure source connections the device will be conditioned to operate the door according to the opposite hand.

It is to be understood that when the breakaway pins are engaged in either the aforementioned set of recesses and under normal operating conditions, the spindle ange 47 and the crank plates 73, 75 and 77 will be rotated together and only upon direct application of force on the crank pins 99 and 101. Otherwise the crank plate assembly is held fast, against movement, by the iluid trapped in the hydraulic unit Z3, as will be later explained, and hence manual operation of the door will cause the breakaway action without displacing the position of the crank assembly.

One ofthe unique advantages of this particular arrangement is that it provides not only an operator capable of positive operation in either direction with both handed door swings, but also provides complete breakaway facilities for emergency conditions and in either direction.

To appropriately actuate the door for movement to the open position or to the closed position, the operator is provided with a twin cylinder power unit indicated generally at 2S. More particularly, the power unit has twin cylinders 131 and 133 which are identical and are formed in parallel in a single block 135 made to ht within the casing 4. The bores of the two cylinders extend from end to end of the block 135 and the rear end of the block nearest inner casing end wall 12 is closed by a header and support member 137, which in turn is appropriately provided with means which permit the cylinder block 135 to be bolted thereto. As shown in FIGS. 3 and 3A, the header 137 is provided with annular recesses 134 and 136 on the face abutting the cylinder block in which a suitable seal, such as an O-ring, may be placed, the recesses being of larger diameter than the cylinder bores and respectively concentric therewith.

As shown, the cylinder support or header 137, on the rearward side, is provided with two outwardly extending bosses 139 and 141 each of which has an internally threaded bore 142 extending through the header and aligned with the axis of a respective cylinder. Short nipples 143 and 145 extending through appropriate openings in end wall 12 of the casing 4 are threaded into the bosses 139 and 141 and drawn up tightly, and then hexagonal nuts 147 and 149 are threaded onto the protruding ends of the nipples 143 and 145, and drawn up against the casing outer wall, to iirmly secure cylinder block and support assembly to the end wall 12 of the casing.

The two substantially identical connecting rods 27 and 27a are connected between the respective crank pins 101 and 99 and respective pistons 153 and 155 operating in the cylinders 131-133. rThe pistons 153 and 155 are of a conventional type and may include an O-ring 156 to prevent leakage of pressure fluid into the casing 4.

Each of the cylinders is provided with three longitudinally spaced ports 157, 159 and 161 (FIG. 2) adjacent the rear end, which ports communicate with counter bores 163, 165 and 167, respectively, extending through a boss 168 formed integrally with the cylinder structure. A conical seat is formed at the juncture of each of the ports and the corresponding counter bore to provide valve -K seats for respective needle valves 169, 171 and 173 each of which is threadedly received within the respective counter bore and is accessible from the upper surface of the boss 168 for regulating the flow of fluid through the respective port. Each of the counter bores 163, and 167 communicates with a longitudinal bore 174 which communicates with a corresponding bore 175 in the cylinder support member 137.

The ports and bores above described in connection with cylinder block 135 may be referred to for convenience as the outlet or exit passages which permit and regulate the ilow of fluid 'from the interior of the cylinder when the respective piston is being moved rearwardly in the cylinder in the direction toward the header 137.

Each of the cylinders is supplied with pressure uid by way of the aforementioned bores 142 in the bosses 139 and 1411 which are connected to an external source of pressure uid such as a suitable pump, not shown. Such fluid is forced through the central passages 142 extending through the cylinder block and past ball check valves 179 each seating within a respective counter bore 183 at the inner end of the passage 142 to permit theflow of fluid into the cylinders but preventing reverse flow therefrom. The return of fluid from each of the cylinders through the ports 157, 159 and 161 and the connecting passage 17d, is completed through the bores 175 in the cylinder support which intersect respective vertical passages 191 and 193, which in turn dump into the previously described horizontal passages 142 on the rearward side of the ball checks 17 9. The upper ends of passages 191 and 193 are closed by suitable needle valves 192 and 194 which are adjustable to control iow from the respective passage 175.

To effect an efficient bleeding of the system the cylinder support -is further provided with la pair of lateral, horizontal passages `195 and 197 which communicate with the vertical passages 191 and 1193, respectively, and lead into an intermediate vertical passage Z113 which opens to the top suriace of the support. The passage 195 intersects an extension of passage 191 below passage 142 and its outward end at the side of the cylinder support is closed by a plug 197. The other horizontal passage 199 intersects the passage `193 above the respect-ive passage |142 and its outer end at the adjacent side of the support body is closed by a plug 21E-1. (See FlGS. 3, 3A and 3B.) The vertically extending passage 2193 terminates upwardly in a counter bore 265 which extends below the juncture with the passage 199, and the inner end of the counter bore provides a seat yfor .a needle valve 207 to .control fluid iiow between the lateral passages 195 and 199. Normally the valve 2117 will be closed. This bleed passage arrangement permits quick and easy bleeding of the hydraulic system when the closer is installed and at any other time it may Ibe required.

A further improvement embodied in my present invention is a novel means for providing continuous protection against possibility of pressure overload .in the hydrauliic system. This means comprises a unique crossover safety valve which is shown in detail FIGURES l, 2, Y4 and 4A.

This improved crossover safety valve is adapted to be installed between the fluid pressure supply lines, leading to and from the door operator, to prevent a pressure buildup within the lines such as would result from -freezing of the internal operator mechanism either from malfunction or as the result of the door movement becoming impeded by some object in the path of the door. Obviously, if the pressure buildup continued it would place an undue strain upon the fluid lines, or result in undesired operation of the breafkaway means, yand could result in damage to the pump mechanism.

ln the `torni shown the new crossover safety valve cornprises a single body or block provided with a pair of forwardly extending, laterally spaced and externally threaded mounting nipples 299 and 211, which are spaced apart on the same axis centers as the bosses 139-141 of the 7 header and support member 137. Each ofthe mounting nipples is formed with a central bore extending through the valve body to the opposite end thereof where the two bores, 217 and 219, are counterbored and 'internally threaded to receive a suitable line connector, such as the type shown at A and B in FIGURE 1. Thus during norrnal operation, the uid lllowing through the pressure supply and return lines will flow unimpededly Ibetween the fluid source and the hydraulic unit 2S through the safety valve.

However, extending vertically upwardly from the aforementioned passages 217 and 219, are a pair of passages 213 and 215 which open to the top of the valve body and each of these passages is counterbored, as at 221 and 223 respectively, to receive a spring loaded valve member 225 and 227 which seats at the lower end of the counterbore to normally close passages 213 and 215. The respective springs 228 are adjusted for tension by means of screws 229 and 231, threadedly received within the respective counterbores 221 and 223, to cause the valve seats to resist upward or unseating movement until a predetermined pressure condition, within the respective fluid lines 217 and 219, is exceeded.

As shown in FIGS. 1, 4 and 4A, each of the counterbored passages 221 and 223 is cross connected to the opposite side ofthe safety valve by means of a respective lateral passage, formed in the valve body by transverse bores 233 and 235, each of which bores is drilled from a respective side of the valve body so as to intersect the respective counterbored passage and terminate forwardly f the opposite counterbored passage where the lateral passage intersects a second vertical passage leading lto the opposite main passage.

Thus, lateral passage 233 intersects counterbore 229 and extends diagonally to a vertical passage 237, directly forward of the counterbore 231; and lateral passage 235 intersects counterbore 231 and extends diagonally across the valve body to a second vertical passage 239, located forwardly of counterbore 229. The vertical passages 237 and 239 lead directly to the main passages 219 and 217, respectively; and since the lateral passages 23S- 235 cross each other, as shown in FIG. 1, one is formed above the other so that they are entirely independent of each other. It will be understood that the outer ends of the drilled lateral passages 233-235 are closed and sealed by suity able plugs 236 and 238, respectively.

In the operation of the cross-over safety valve, any excess of pressure in one main `line will lift the respective plunger valve and permit the pressure fluid to ow through the respective lateral passage to the opposite vertical passage and thence to dump into the other main passage which would then be functioning as a return line to the pressure source.

In FIGURE 1 the crossover valve is shown connected to the nipples 143 and 145 by means of universal couplings 249 and 2511. Line connectors A and B are then connected to suitable fluid supply lines, not shown, which in turn .are connected to a suitable iluid pressure source, or pump, also not shown, capable of forcing fluid under pressure alternately through either one of the supply lines while withdrawing fluid from the other supply line. A suitable fluid pressure source for use with the present invention may be either of those disclosed in my Patent No. 2,927,429 and my copending application Serial No. 44,156, led July 20, 1960, now Patent No. 3,043,277.

In operation, the subject operator is installed beneath the floor surface adjacent the door with the spindle 30 appropriately keyed to the door and serving as one of the door pivots. Appropriate fluid supply lines are then connected to the line connectors A and B; the supply lines being connected in a closed -uid pressure system including a pump and valving means adapted to change or reverse the direction of uid flow through the respective lines in response to a suitable external actuating means,

8 such as an electric eye 'or an electric door mat, either being appropriately utilized to initiate door opening and door closing operation in response to the position of a person using the door opening. In any case, with the improved door operator mechanism, both opening and closing operations of the door are power driven, thus assuring positive door operat-ion throughout the entire opening and closing cycle.

As shown in FIG. l, the operator mechanism is arranged yfor right hand `door opening operation, the hand being determined by the direction in which the door swings, i.e. to the r-ight or to the left, upon opening for a person Ifacing a door swinging away from him, and the elements are shown in the position they assume when the door is opened. Thus, the piston 155 has reached the end of its power stroke in the cylinder 133, the door has been swung `from its centered position `indicated bythe line C to the full open position indicated by the line D, the movement of the crank plate assembly has been arrested by engagement of the stop screw 89 with the casing ange shoulder l16, and the mechanism is locked in this opened door position by the fluid trapped behind the piston 155 and in the tluid supply system.

Upon appropriate operation of the safety mat, or electric eye, on the leaving side of the door passage, the fluid pressure supply means will be actuated in the reverse direction of fluid flow to drive the piston 153 forwardly from its cylinder 131 to thereby rotate the crank plate and spindle assembly, in the counter-clockwise direction, to close the door which, upon reaching its centered position, line C, will then be stopped by engagement of the stop screw with the casing flange shoulder 18. Fluid trapped behind the piston 153 will then hold the door in its `closed position.

In either case, both opening `and closing, the speed of door movement yis controlled by the speed control valve means 168; there being one for each cylinder, and appropriate adjustment of the needle valves therein, to govern the rate of uid discharge from the cylinder as its piston is moved inwardly, will determine the speed of door movement during the opening and closing phases of its operation cycle. In the event that some impedance inter-feres with swing of the door in either direction, the actuating fluid pressure will build up in the power supply line and unseat the respective plunger valve, 225 or 227, and allow automatic by-pass Aof the pressure Huid to the opposite line. Normally this by-pass of pressure uid will occur before sufficient force is applied to the driving piston to cause operation of the breakaway means connecting the crank plate assembly 26 to the spindle ange 47.

Because of the leverage advantage involved, a moving 'force -applied manually to the door, by a person of average strength, will cause the breakaway system to operate. Thus the breakaway means serves not only to permit opening of the door under emergency or panic conditions and when the operator mechanism is inoperative, but also as the means for reversing the hand of operation for the door operator mechanism.

When it is desired to change the hand for the operator mechanism, from thc right hand operating condition as shown to a left hand operating condition, it is only necessary to manually swing the door so as to turn lthe spindle 30, 90 degrees in the counter-clockwise direction as viewed in FIG. 1. This will be done after the operator has been installed and operatively connected with an operative lluid pressure source, and after the operator has been actuated to swing the door to the Vopened position indicated `by the Ibroken line D. The

door will then be returned to its centered position, indicated by the broken line C, the crank plate assembly remaining in the position shown in PIG. l, and the spindle `lian-ge will have become shifted so that the breakaway pins 105-107-109 of the crank plateassembly will engage in the sockets t123:--125 and 127, respectively, 'of the spindle flange. The iiuid pressure supply system connections will then be reversed, or the electrical controls yfor the pressure supply system will be reversed, and the next operation of the opera-tor mechanism will swing the door on the spindle 39 in the left hand operating direction, or counter-clockwise as viewed in FIG. l, for its opening movement.

It will be Iunderstood that if the operator mechanism is initially conditioned Afor :left hand opening operation of the door, wherein the breakaway pins are engaged in the spindle flange sockets l23l25-127, a change to right hand door operating condition will be accomplished by swinging the door manually to turn the spindle 90 clockwise while the crank assembly is stationary.

Gne method of operating the improved door operator mechanism is to provide a fluid pressure supply pump that is unidirectional in its operation and utilizes a 4-way reversing valve for directing the pressure supply to one side of the operator to open the door and then to the other side of the operator to iclose the door. in such a case the 4-way reversing valve will be controlled for position, or pressure flow direction, by the electric floor mats or the electric eye means ordinarily used for vdoor operator actuation and control; and the pump motor will include a suitable timer in its control circuit so :that once it has been started for a door operating lcycle it will continue to run until the operator mechanism has been inactive` for a predetermined period, .at which time the motor will stop until reactivated by a person using the door. Under these conditions the hydraulic unit of the door operator will be under constant pressure, on one side or the other, as long as the pump motor is running and, when the door is at the end of its movement in either direction, relief of driving pressure on the hydraulic unit will be had by automatic operation of the safety crossover valve interposed between the pump and the hydraulic unit of the operator as previously described. Suitable control circuits for such a method of dooroperator operation are known and understood by those skilled in this art; and suitable components, such as valves and timers, are readily obtainable in the present market as standard items yfor such use.

An alternative metlhod for operating the improved door operator mechanism is to provide internal limit switch means for automatically stopping the pump motor when the door is fully opened and again when the door is fully closed, in each case the pump motor being re-started by operation of the safety mat or electric eye at the exit side of the door and by operation of the actuating mat or electric eye at the entrance side of the door. Such a limit switch means is diagrammatically shown in FIG. l at E where two pairs of normally closed switch contacts, 251-255 and 253-257, are indicated. Contacts 25l` and 253 are movable members adapted to be actuated by an element 25% projecting laterally from the connecting rod 27, and Vcontacts 255 and 257 are fixed members. Each pair of contacts is appropriately mounted in the casing d so that the contacts 252l-255 will .be opened by the element 259 when the mechanism is at the door closed position, and contacts 253-257 will be opened when the door is at the open position as shown in FIG. l. AS shown, contacts 251 and 253 are connected to a common terminal and contacts 255 and 257 are connected to separate terminals each of which leads to an appropriate relay in the pump motor control circuit, not shown.

From the foregoing description it will now be seen that an improved door operator has been provided which includes an internal mechanism sufficient to accomplish a multiplicity of functions and yet be non-handed, in the sense that the internal mechanism may be easily and efiiciently adjusted, without opening the operator casing and even when installed, to provide either a right or left handed door opening movement. Other advantages of this invention reside in the fact that the improved device provides an effective non-handed door operator of the type described which is externally adjustable through the wide range of values in order to achieve substantially any desi-red speed of door closing and opening movement during all operating phases :and in both directions of door swing; in the improved adjustable stop means for limiting the maximum open and closed positions of the internal operating mechanism of the device during both normal and panic operations of the door which means is adapted to accommodate both right and left ihanded conditions of operation of the device; in the fact that the improved door operator is simple in operation, manufacture, and repair and is inexpensive to maintain; and in the improved crossover safety valve feature on the hydraulic side of the operator mechanism which serves to fully protect the mechanical elements, the pump, and the supply lines, regardless of the direction of door swing for which the mechanism may operate and in all phases of an operation cycle.

Although but one specific `embodiment of this invention has been herein shown and described it will be understood that numerous details of the construction shown may be altered or omitted without departing from the spirit of the invention as defined by the following claims.

1 claim:

l. A door operator mechanism, comprising a casing having upwardly extending side and end walls, a spindle rotatably mounted in said casing on a vertical axis for controlling the opening and closing movement of a door supported axially on said spindle, a radial flange member carried by said spindle within said casing and having driving connection with said spindle, a crank plate member rotatably mounted on said spindle within said casing, breakaway means mounted on one of said members and having a releasable driving connection with the other member to provide a first driving position therebetween for rotation of said spindle in a predetermined direction of door opening movement, said breakaway means being adapted to hold a maximum torque and to be releasable to permit relative rotation of said members when said torque is exceeded, means on said other member for drivably engaging said breakaway means upon relative rotation of said members through an angular distance degrecs to establish a second driving position between said members, reversible fiuid pressure actuated means for riving said crank plate member alternately in opposite directions of rot tion about the axis of said spindle, coacting stop means on said casing walls and on said crank plate member for limiting the rotation of said crank plate member to the said angular distance between the first and second driving positions of said flange member therewith, and coacting stop means on said flange member and on one of said casing walls for limiting the rotation of said spindle independently of said crank plate.

2. A door operator mechanism comprising a casing having upwardly extending side and end walls, a spindle rotatably supported in said casing on a vertical axis for controlling the opening and closing movement of a door carried axially on the spindle in driving relation therewith, a radial frange fixed on said spindle within said casing, a crankplate rotatably journaled on said spindle adjacent said ange, coacting stop means on said casing walls and on said crankplate for limiting the rotation of said crankplate to the extent of the opening and closing movement of the door, other coacting stop means on said spindle ange and on one of said casing walls for limiting the extent of rotation of the spindle and arranged to permit said spindle to rotate through a greater angular distance than said crankplate, breakaway means extending between said flange and said crankplate and providing a first operative driving connection therebetween, said breakaway means being adapted to release said first driving connection under a predetermined maximum condition of torque and permit relative rotation of said flange and crankplate, means angularly spaced from the position of said first driving connection 'for coacting with said breakaway means to establish a second operative driving connection between said flange and said crankplate when said spindle is rotated beyond the limits of angular movement of the crankplate, and power means connected to said crank plate for rotating said crankplate alternately in one direction and then the other direction, said breakaway means being adapted to release said second driving connection only when said maximum condition of torque is exceeded.

3. A door operator mechanism comprising a casing having upwardly extending side and end walls, a spindle rotatably supported in said casing on a vertical axis for controlling the opening and closing movement of a door carried axially on the spindle in driving relation therewith, a radial ange member iixed on said spindle within said4 casing, a crankplate member rotatably journaled on said spindle adjacent said flange member, coacting stop means on said casing walls and on said erankplate member for limiting the rotation of said crankplate member to the extent of the opening and closing movement of the door, other coacting stop means on said spindle ange member and on one of said casing Walls for limiting the extent of rotationof said spindle and arranged to permit said spindle to rotate through a greater angular distance than said crankplate member, breakaway pins on one of said members extending axially toward the adjacent face of the other member, said pins being spring biased toward said other member, pin engaging means on said other member for releasably engaging said pins to provide a first operative driving connection between said members, said pins being conditioned to release said first driving connection under a predetermined maximum condition of torque and permit relative rotation of said members, and

other pin engaging means on said other member spaced approximately ninety degrees angularly from the position of the iii-st mentioned pin engaging means to establish a second operative driving connection between said members when said spindle and tiange member are rotated approximately ninety degrees` angularly relative to the crankplate member, said second driving connection being releasable only when said maximum condition of torque is exceeded.

4. A door operator as defined in claim 3 wherein a reversible power means is connected to said crankplate member for driving said crankplate member rotatably in alternately opposite directions.

5. A door operator as defined in claim 3 wherein a fluid pressure actuating means is connected to each of diametrically opposite sides ofthe crankplate member for rotatably driving the same first in one direction and then the other, and said uid pressure means comprises a pair of independent cylinders each having a piston therein connected to a respective side of said crankplate, and means for supplying pressure tluid to each of said cylinders selectively.

References Cited in the file of this patent UNITED STATES PATENTS 2,234,008 Price Mar. 4, 1941 2,590,454 Pilch Mar. 25, 1952 2,628,731 Reuter Feb. 17, 1953 2,750,931 Penrod et al June 19, 1956 2,869,861 Carlson Jan. 20, 1959 2,927,429 Carlson Mar. 8, 1960 2,985,142 Aiken May 23, 1961 3,064,426 Furia et al Nov. 20, 1962 

1. A DOOR OPERATOR MECHANISM, COMPRISING A CASING HAVING UPWARDLY EXTENDING SIDE AND END WALLS, A SPINDLE ROTATABLY MOUNTED IN SAID CASING ON A VERTICAL AXIS FOR CONTROLLING THE OPENING AND CLOSING MOVEMENT OF A DOOR SUPPORTED AXIALLY ON SAID SPINDLE, A RADIAL FLANGE MEMBER CARRIED BY SAID SPINDLE WITHIN SAID CASING AND HAVING DRIVING CONNECTION WITH SAID SPINDLE, A CRANK PLATE MEMBER ROTATABLY MOUNTED ON SAID SPINDLE WITHIN SAID CASING, BREAKWAY MEANS MOUNTED ON ONE OF SAID MEMBERS AND HAVING A RELEASABLE DRIVING CONNECTION WITH THE OTHER MEMBER TO PROVIDE A FIRST DRIVING POSITION THEREBETWEEN FOR ROTATION OF SAID SPINDLE IN A PREDETERMINED DIRECTION OF DOOR OPENING MOVEMENT, SAID BREAKAWAY MEANS BEING ADAPTED TO HOLD A MAXIMUM TORQUE AND TO BE RELEASABLE TO PERMIT RELATIVE ROTATION OF SAID MEMBERS WHEN SAID TORQUE IS EXCEEDED, MEANS ON SAID OTHER MEMBER FOR DRIVABLY ENGAGING SAID BREAKWAY MEANS UPON RELATIVE ROTATION OF SAID MEMBERS THROUGH AN ANGULAR DISTANCE 90 DEGREES TO ESTABLISH A SECOND DRIVING POSITION BETWEEN SAID MEMBERS, REVERSIBLE FLUID PRESSURE ACTUATED MEANS FOR DRIVING SAID CRANK PLATE MEMBER ALTERNATELY IN OPPOSITE DIRECTIONS OF ROTATION ABOUT THE AXIS OF SAID SPINDLE, COACTING STOP MEANS ON SAID CASING WALLS AND ON SAID CRANK PLATE MEMBER FOR LIMITING THE ROTATION OF SAID CRANK PLATE MEMBER TO THE SAID ANGULAR DISTANCE BETWEEN THE FIRST AND SECOND DRIVING POSITIONS OF SAID FLANGE MEMBER THEREWITH, AND COACTING STOP MEANS ON SAID FLANGE MEMBER AND ON ONE OF SAID CASING WALLS FOR LIMITING THE ROTATION OF SAID SPINDLE INDEPENDENTLY OF SAID CRANK PLATE. 